EP0751027B1 - Disposition of a hydrodynamic clutch within a drive system - Google Patents

Description

The invention relates to an arrangement of a hydrodynamic coupling in a drive system, in particular a turbo compound system, in detail with the features from the preamble of claim 1.

In turbo compound systems, the recovery of Energy from the exhaust gases of an internal combustion engine Exhaust gas turbocharger provided one of the engine exhaust driven turbine and one with it mechanically connected compressor, and which for the engine the required combustion air is pre-compressed. The exhaust gases even own after flowing out of the turbine a high energy content. To use this residual energy make it possible to use the turbine of the Exhaust gas turbocharger a second, driven by the exhaust gases Subordinate turbine, which is switched so that a part the residual energy mechanically on the drive shaft of the Internal combustion engine or an associated drive transmits.

1. US-PS 4,586,337

2. WO 86/00665

Such systems are known, for example, from the following publications:

1. U.S. Patent 4,586,337

2. WO 86/00665

These two documents show exhaust gas turbines that have a hydrodynamic clutch from the exhaust gases of a Internal combustion engine gained energy on a steering wheel of the motor and for a vibration decoupling between engine and exhaust gas turbine.

With these turbo compound systems it is important that Losses in the transmission between the exhaust gas turbine and minimize the crankshaft to ensure that the Residual energy is a really additional driving force on that Crankshaft transmits. It is beneficial that Lubricant of the engine as an operating medium to use hydrodynamic coupling. In this case can hydrodynamic clutch bearing simultaneously can be lubricated, and the engine oil pump can be used to fill the hydrodynamic clutch can be used, and at the same time can with the lubricant with constant flow generated heat are dissipated.

Wear the main bearings in a hydrodynamic clutch on one side the turbine wheel and the pump wheel and on the other the stationary part of the coupling. Because of of constant rotation are the bearings which Support the turbine wheel against the pump wheel, only that Slip between the pump and the turbine wheel exposed to hydrodynamic coupling. These camps, which support the turbine wheel against the pump wheel are therefore referred to as low-speed bearings. The bearings, which are both the pump wheel or the turbine wheel support in the stationary part of the clutch, are constantly stressed with rotation, especially with higher ones Speeds. These camps are therefore Called high speed warehouse. In US 3,058,296 and US 3,136,129 are both low and low High speed warehouse - flooded with one Oil / hydraulic fluid, which is in the working space of the clutch is directed. There are therefore very large currents for heat dissipation required because the heat generated at the bearings must be dissipated.

EP 0 507 887 B1 therefore describes an arrangement for effective oil supply to a working chamber in one with oil flowed through hydrodynamic coupling and for lubrication the bearings of the clutch known, the oil supply through causes a channel in the standing part of the coupling that is in a space of the clutch upstream of a first bearing opens, through which the impeller in Impeller of the clutch is mounted, the oil after Flow through the first bearing which the impeller and Working chamber of the clutch containing the impeller has been reached. The clutch is in one of the wheels for storage in the housing a second camp arranged with the room upstream of the first bearing via a throttle in Connection is established, the throttle against the main oil flow seals for coupling and only one for flow lubrication of the second bearing allows enough oil to pass through. A Such an arrangement is characterized by an enormous constructive effort. For the supply of resources one camp completely flooded while the other Bearing via a throttle a partial flow for lubrication is branched off. Because of this arrangement and one complicated resource supply channel routing due to the Resource management from a stationary component to one rotating component are a number of additional Sealing measures required.

The invention is therefore based on the object hydrodynamic coupling for use in one Drive system, in particular turbo compound system, such to develop that simple resource supply takes place and none for the lubricant supply to the bearings separate supply line is required. The due the torque transmission in the clutch Heat should be dissipated without much effort can.

The solution according to the invention is characterized by Characterized features of claim 1. Beneficial Refinements are given in the subclaims.

According to the invention, the primary, i.e. of the pump wheel of the hydrodynamic coupling on the Output shaft of the clutch with which the secondary or the turbine wheel can be connected in a rotationally fixed manner. The support preferably takes place via a bearing arrangement, comprising at least one bearing, preferably two bearings, preferably due to the good receptivity for combined loads angular contact ball bearings can be used. The angular contact ball bearings are placed side by side in pairs arranged. The arrangement of this storage takes place in radial direction below that described by the impeller Workspace part. In the axial direction in the installation position viewed the arrangement of the storage preferably takes place in the area of the parting plane, which depends on the blading of Pump wheel and turbine wheel is formed. For Resource supply is a by itself Output shaft extending central bore provided by which is in the radial direction in the circumferential direction Output shaft extend distribution channels. These are preferably arranged in the installed position of the coupling, that this also in the area of the parting plane between Turbine and pump wheel lie. The distribution channels open into one of pump and turbine wheel in installation position described and the toroidal work space upstream feed space. As already mentioned, this in the axial direction from the turbine wheel and on the part of the Pump wheel essentially from the bearing arrangement limited. To implement a partial flow branch for the bearing arrangement are corresponding means in Equipment supply space provided. these can for example in the form of a disc with a cross section beveled inner contour. The result resulting passage serves the dosage of Lubricant flow through the bearings.

The solution according to the invention is characterized by a simple structure, especially a simple one Equipment supply with simple ducting, whereby in Resource supply system at the same time Branch option for the lubricant supply to the bearings is provided. Elaborate sealing measures can omitted. The resources are supplied here during operation about rotating machine parts. Additional sealing measures are not required. The solution according to the invention is Very easy to implement in terms of production technology and thus inexpensive. Furthermore, it is characterized by a easy assembly and therefore also later interchangeability out.

Advantageously, there is also the possibility of Branch of the partial flow for the bearing arrangement Supporting the impeller also for this partial flow Lubrication adjacent in the axial direction in the area of Bearing arrangement to use arranged bearings. You can do this simple connecting lines or holes or openings be used.

When the equipment heats up, it can over Openings on the turbine wheel are removed and replaced by new ones Operating equipment, which via the central supply line fed back into the work area through the output shaft will be replaced.

With appropriate storage arrangement and arrangement of funds for metering the partial flow, this can be a percentage compared to the existing equipment in the work area be kept as low as necessary.

Figur 1 zeigt eine erfindungsgemäße Ausführung einer Anordnung einer hydrodynamischen Kupplung in einem Turbocompoundsystem mit einer eine Abschälkante bildenden Scheibe im Betriebsmittelzufuhrraum;

Figur 2 verdeutlicht eine weitere erfindungsgemäße Ausführung für die Anordnung einer hydrodynamischen Kupplung.

The solution according to the invention is explained below with reference to figures. It also shows the following:

FIG. 1 shows an embodiment according to the invention of an arrangement of a hydrodynamic coupling in a turbo compound system with a disk forming a peeling edge in the operating medium supply space;

Figure 2 illustrates another embodiment of the invention for the arrangement of a hydrodynamic clutch.

Figure 1 illustrates one for power transmission belonging hydrodynamic coupling 1 in detail. The hydrodynamic clutch 1 comprises a primary wheel, which is referred to as an impeller 2, and a turbine wheel secondary wheel which becomes effective and which has the reference number 3 is designated. Pump and turbine wheel form together a toroidal work space 4, which with Operating fluid, for example, can be filled with oil. The Pump wheel is from one to one not shown here Shaft of a drive turbine, not shown here arranged gear driven. Combs for this purpose this gear with a rotationally fixed with the pump wheel 2 coupled gear 5.

The secondary wheel or turbine wheel 3 is on one Output shaft 6 of the hydrodynamic clutch 1 arranged. In the exemplary embodiment shown, the turbine wheel is 3 with the output shaft 6 rotatably by means of force or positive connections in the form of Screw connections, here the representative Screw connections 7 and 8, coupled. The over the hydrodynamic coupling 1 on the output shaft 6 Power transmitted to a power transmission unit transferred, which via the output shaft 6 to the Power transmission unit transferred power with the Power on the output shaft one is not here shown engine in the area of Power transmission unit is added. Furthermore are on the output shaft 6, the gear 5 via a bearing 9, which is designed for example as a ball bearing, and the impeller 2 via an arrangement of a sleeve 10 and a bearing arrangement 11 stored. The bearing arrangement 11 includes two angular contact ball bearings 12 or 13. These allow combined loads, i.e. Radial and axial forces better than deep groove ball bearings to record. The pump wheel 2 is supported by the sleeve 10 and the two angular contact ball bearings 12 and 13 on the Output shaft 6 from. For this purpose, the inner rings 14 or 15 of the angular contact ball bearings 12 or 13 of the bearing arrangement 11 arranged directly on the output shaft 6. The Outer rings 16 and 17 of the angular contact ball bearings 12 and 13 respectively Bearing arrangement 11 are supported on the inside 18 of the Sleeve 10 off. The primary wheel 2 is on the outside 19 the sleeve 10 in contact. To realize the Torque absorption on the pump wheel and transmission via the Operating resources on the turbine wheel 3 are rotated of impeller 2, sleeve 10 and the outer rings 16 and 17 of Angular contact ball bearings 12 and 13 with the same speed. Between the outer rings 16 and 17 and the sleeve 10 and the Outside 19 of the sleeve 10 and the impeller 2 are closed press seats provided for this purpose. The same applies to the Support of the gear 5 on the bearing 9 on the Output shaft 6.

The oil supply to the work area is direct via the output shaft 6. For this purpose, the Output shaft 6 has a bore 20, which is preferably arranged coaxially to the axis of symmetry A of the output shaft 6 is. This hole extends from the primary side to roughly to the through the perpendicular through the toroidal work space level. Of this Central bore 20 go from distribution bores 21 and 22, which is from the central bore 20 to the Outer periphery 23 of the output shaft 6 in the radial direction extend. Via the central bore 20 and Distribution holes 21 and 22, the operating fluid in the toroidal workspace 4 directed. At the same time a branch of the oil flow for the bearing arrangement 11. Zu this purpose is between the pump wheel 2 and the turbine wheel 3 a disc 24 is arranged, which is a beveled Has inner contour 25 which as a peeling edge for Resource acts. The bevelled inner contour runs from the feed chamber 26 to the outer rings 16 and 17 of the angular contact ball bearings 12 and 13 of the bearing arrangement 11 there. The two angular contact ball bearings 12 and 13 are thereby completely flooded. According to the interpretation of the Washer 24 can be branched to the size Equipment flow can be influenced. So it is only a central supply of equipment and thus also Lubricant supply required. With appropriate Configuration there is also the possibility of the bearing 9, which is the support of the gear 5 on the output shaft 6 is used to supply lubricant.

The hydrodynamic clutch 1 is one bell-shaped housing 27 enclosed. This is preferably designed as a deep-drawn part and by means of various connection options on the gear 5 attached. This gives you the opportunity to to produce bell-shaped housing 27 as a deep-drawn part and for example by welding or To fasten tack connections to gear 5.

FIG. 2 shows an embodiment similar to that in FIG Figure 1 shows why the same elements same reference numerals were used. The impeller of the hydrodynamic clutch 1 is also supported here by a Bearing arrangement 11, comprising two arranged in pairs Angular contact ball bearings 12 and 13 on the output shaft 6 of the hydrodynamic clutch. The impeller 2 is the another rotatably connected to a gear 5, here via the screw connections 7 and 8. The gear 5 is supported partly from the angular contact ball bearing 13.

The turbine wheel 3 is connected via a spline connection 30 the output shaft 6 rotatably coupled. The supply of the Working room 4 with operating fluid takes place via a Central bore 20 which extends from the secondary side, i.e. from the side of the turbine wheel 3, in the direction of the primary side, i.e. in the direction of the impeller 2, the hydrodynamic Coupling 1 extends through the output shaft 6. Of this Central bore 20 extend distribution channels 31 and 32 in the radial direction to the outer circumference 23 of the Output shaft 6. The distribution channels 31 and 32 are there arranged such that they are radial in the axial direction below the impeller 2, in particular the Resource supply space 26 are arranged. The Operating fluid passes from the operating fluid supply space 26 directly to the bearings 12 and 13 of the bearing arrangement 11. Also in this case, a flow of equipment for lubrication the bearing of the equipment room 26, which in the Workroom 4 opens out, branches off.

In the embodiment shown there are further distribution channels 33 and 34 provided a further bearing 35 from the Central bore 20 can supply with lubricant. In another variant not shown here the possibility of this camp 35 also branched off To supply equipment flow from the supply space 26. To this purpose is a connection between the bearing 13 of the Bearing arrangement 11 and the bearing 35 required. The three In this case, bearings could be branched off Resource flow can be supplied from.

The bell-shaped clutch housing 27 is here arranged and executed that it directly with the primary wheel connected is. Again, this is bell-shaped Coupling housing 27 designed as a deep-drawn part.

The turbine wheel 3 is constructed and constructed such that it in the installed position in the equipment supply space 26 protruding ribs. These are like this arranged that they are at certain intervals on a common diameter in the lubricant supply space are arranged.

The arrangement of the resource supply space 26 enables it also, the spline connection between turbine wheel 3 and lubricate output shaft 6.

Claims (5)

1. Arrangement of a hydrodynamic clutch in a drive system, in particular a turbocompound system;

   1.1 the hydrodynamic clutch comprises a pump wheel (2) and a turbine wheel (3) which together form a toroidal working chamber (4);

   1.2 the turbine wheel is non-rotatably connected to a driven shaft (6);

   1.3 an operating medium supply system is associated with the toroidal working chamber;

      characterised by the following features:

   1.4 the pump wheel is supported on the driven shaft via a bearing arrangement (11);

   1.5 the operating medium supply system comprises:

   1.5.1 an operating medium supply chamber (26) which is arranged radially below the toroidal working chamber and is limited axially from the bearing arrangement and the contour of the turbine wheel;

   1.5.2 a central operating medium supply channel (20) which is arranged in the driven shaft and extends axially in the driven shaft at least into the region of the centre plane of the clutch;

   1.5.3 at least one distributing channel (21, 22; 31, 32) which connects the central operating medium supply channel to the operating medium supply chamber;

   1.6 means (24) are provided in the operating medium supply chamber to allow metered branching of a partial flow for lubrication of the bearing arrangement.
2. Arrangement according to claim 1, characterised in that the medium is a disc (24) which adjoins the outer ring (17) of the bearing arrangement for supporting the bearing in an axial direction in the operating medium supply chamber and clears an orifice extending in the direction of the bearing.
3. Arrangement according to one of claims 1 to 2, characterised in that the bearing arrangement comprises two rolling bearings (12, 13) arranged side by side.
4. Arrangement according to claim 3, characterised in that the two rolling bearings (12, 13) are designed as annular-contact ball bearings.
5. Arrangement according to one of claims 1 to 4, characterised in that a further bearing (35) is provided for supporting the driven shaft on a machine part which is connected to the central operating medium supply channel (20) via at least one channel (33, 34) for lubricant guidance.

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